Machine tool control



June 24, 1947. c, JOHNSON ncnnm r001. comnor.

Original Filed Sept. 23, 1941 2 Sheets-Sheet 1 CLARENCE JOHNSON 0- 2. T E (NM. A WHMHHMH. W 2 on. Eu. bk

June 24, 1947.

Original Filed Sept. 23, 1941 2 Sheets-Sheet 2 ll n I I82 4 H1 80 1 G an? "I '90 m I83 is we -ISO I65 I53 ISI :55

I45 '55 i Inventor .59

FIG. 5

CLARENCE JOHNSON Patented June 24, 1947 MACHINE TOOL CONTROL Clarence Johnson, South Euclid, Ohio, assignor to Bailey Meter Company, a corporation of Delaware Original application September 23, 1941, Serial No. 412,017, new Patent No. 2,372,427, dated March 27, 1945. Divided and this application February 1, 1943, Serial No. 474,273

This invention relates to duplicators or profilers as they are sometimes called, for machine tools. such as lathes, slotters, planers, milling machines, die sinking machines, and the like.

One object of my invention is to provide an improved duplicator in which a work piece and a tool are moved relative to each other to cut the work piece to a desired shape.

Another object is to provide a duplicator having means for effecting relative bodily movement between a cutting tool and a work piece, and also having means for rotating the work piece at variable speeds so as to maintain a substantially constant cutting speed.

Still another object is to provide a duplicator having means for moving a cutting tool and a. work piece relative to each other in such a way that the latter is cut to a desired shape while the cutting speed is maintained substantially constant.

One object of my invention is to provide a duplicator wherein the linear cuttin speed of the tool relative to the work is maintained constant or varied in predetermined manner.

Further objects will be apparent from the description and drawings in which:

Fig. 1 is a plan view of an engine lathe having my invention incorporated therein.

Fig. 2 illustrates diagrammatically a part 01' the control circuit employed in the embodiment of my invention shown in Fig. 1.

Fig. 3 is a plan view of a milling machine illustrating the application of my invention thereto.

Fig. 4 is a fragmentary view to larger size of a part of Fig. 3.

Fig. 5 is a diagrammatic illustration of the control circuits employed in the embodiment of my invention shown in Fig. 3.

As is well understood by those familiar with the art, in some machine tools, such as lathes. the tool is moved longitudinally and transversely of the work piece, which except for rotation about its center remains stationary. In other machine tools. such as some types of milling machines, the work piece may be moved in two directions, while the tool except for rotation about its axis, remains stationary. In some other types of milling machines, and usually in die sinking machines, the tool may be moved in one or more directions and the work piece also moved in one or more directions. In all instances it will be observed. however, that it is the relative movement between the tool and work piece that causes the work piece to be formed to a desired shape. As one specific embodiment I have chosen to illustrate and describe my invention incorporated in a lathe, wherein the work piece except for rotation about its center remains stationary and the tool is moved transversely and longitudinally thereof. As another specific embodiment of my invention I have illustrated my invention applied to a milling machine wherein the tool, except for rotation about its center remains stationary and the work piece is moved in two directions in order that the tool may cut the work piece to a desired shape. It will thus be evident that my invention is applicable to a wide variety of machine tools, and that when I speak of relative movement between the tool and work piece I include either an arrangement where the tool is stationary and the work piece moves. or the work piece is stationary and the tool is moved, or the combination of the two.

This application is a division of my Patent No. 2,372,427, granted March 27, 1945.

In Fig. 1 I show a preferred embodiment of my invention. It is well appreciated that for optimum results the linear speed of a tool relative to a work piece should remain substantially constant or varied in a predetermined manner. That is to say, there is an optimum speed at which the work should be moved past the tool, or vice versa. In cutting operations, particularly turning operations, the linear speed of the work piece past the tool decreases as the tool approaches the center of rotation 01 the work piece, it the headstock is rotated at constant speed. Thus, unless the turning operation is interrupted and the rotary speed of the headstock varied as the diameter of the work piece varies. the turning operation will not be performed at maximum efficiency. It is particularly desirable that the speed of the headstock be automatically varied in accordance with changes in diameter of the work piece when the tool is automatically positioned relative to the work by a master, as such automatic operation dispenses entirely with the necessity of an operator devoting his attention to the operation of the lathe. Not only in so-called turning operations is it desirable that the linear speed of the work piece past the too] be varied, but also in other machining operations, and I illustrate m invention applied both to a. lathe and to a milling machine, wherein for reasons that will be pointed out more in detail hereinafter the speed of the work piece past the tool is preferably varied in predetermined i'ashlon.

Referring to Fig. 1, I therein show the lathe i wherein the tool Ill is automatically positioned transversely oi the work piece l5, as well as longitudinally thereof, in accordance with changes in the shape of the master I0. Additionally thereto I iurther show in Fig. l apparatus whereby the work piece I is rotated at a variable Speed depending upon the radial position or the tool I0. My invention contemplates that the speed with which the work piece i0 is rotated may be varied in any predetermined desired manner. Generally, however, it is thought preferable to have the work piece I0 rotate at an increasing speed as the tool I0 approaches the center of rotation.

Referring to Fig. l, I show the headstock 2 rotated by a hydraulic motor I20 through gears IIIA and I22A. In Fig. 2 I show diagrammatically the fluid control circuit for the hydraulic motor I20. Hydraulic fluid under pressure is transmitted to the motor I20 through a pipe I2I connected to the outlet of a variable fluid resistance I22 which is supplied with hydraulic fluid from a suitabl pump I23 driven by a motor I24. The pump I23 and fluid resistance I22 are for convenience housed in a hydraulic fluid reservoir I20 and the hydraulic fluid discharged from the motor I20 is returned thereto through a pipe I2IIB.

The fluid resistance I22 is disclosed in detail in my Patent 2,372,426 and will be described only briefly herein. This resistance, at some position of the movable member I20, has 9. minimum resistance at which position the flow of oil to the motor I20 will be at maximum, and accordingly the headstock 2 willrotate at maximum speed. It the member I20 is positioned upwardly or downwardly from this position the fluid resistance I22 will increase, thereby causing the motor I20 and headstock 2 to rotate at a slower sp ed.

The position of the member I20 is controlled by an expansible bellows I21 connected through a pipe I20 and 3-way valve I20 to a nozzle I30 carried by the movable carriage I. Air under pressure is supplied the pipe I23 through an oriflce I3I. As the rate of discharge through the nozzle I30 decreases, the pressure within the pipe I20 will increase, thereby causing the bellows I21 to position the member I20 downwardly. Conversely upon an increase in the rate or discharge from the nozzle I30 the bellows I21 will contract, causing the member I20 to move upwardly. causing a corresponding change in the resistanc of the fluid resistance I22.

The rate of discharge through the nozzle I30 is controlled by means of a cam I32 secured to the cross-slide 0. The cam I32 may be given any shape desired, so that the magnitude of the fluid resistance I22, and accordingly the speed of the moto I 20 and headstock 2 will be varied as desired. For reasons heretofore stated it is usually preferable to have the rotative speed of the work piece I0 increase as the tool I0 is positioned toward the center thereof. Accordingly, under usual operating conditions the cam I32 will be provided with a straight taper and adjusted relative to the nozzle or discharge device I30, so that when the tool I0 is at the maximum rs dial distance from the center of rotation of the work piece II the member I20 will be positioned so that the fluid resistance I22 is at a maximum, and thereafter as the tool I0 approaches the center of rotation of the work piece I0 the speed of rotation thereof will increase. It will be evident however, that the cam I32 may be given any shape whatsoever to produce a desired functional relation between the transverse positioning 0! the tool I0 and speed 01' rotation of the workpiece I0.

In order that the fluid motor I20 may be manually operated at any desired speed, I provide the three-way valve I20, which in the position shown places the bellows I21 under the control of the nozzle I30. When the three-way valve I23 is shifted from the stop I33 to a stop I34 the nozzle I30 is shut off from the bellows I21 and a pipe I30 connected thereto which may be supplied with compressed air from any suitable source. Located in the pipe I30 is a control valve I30. The pressure within the bellows I21 and accordingly the speed of the hydraulic motor I20 and headstock 2 may be varied by manipulation of the valve I30, increasing or decreasing the pressure within the pipe I20. I show between the valve I30 and the three-way valve I20 9. bleed port I3! open to the atmosphere, which permits a flow of pressure fluid through the valve I30, and' accordingly it is evident that positioning of the valve I30 will produce corresponding variations in pressure within the pipe I20 and bellows I21.

It is apparent that any suitable tracer mechanism may be employed in the embodiment of my invention shown in Fig. l. I have for clarity diagrammatically shown such a mechanism wherein the nozzles 24 and 20 are carried by a horizontal bar supported on the cross-slide 0 and the master feeler is carried by a substantially parallel horizontal baflle pivotally supported on the carriage I and urged against the shaped profile of the master I0 by suitable spring means. In operation, movements of the banle toward or away from the nozzles 24 and 20 effect desired longitudinal movements of the carriage I and transverse movements of the cross-slide 0.

In Figs. 3, 4 and 5 I illustrate the application of my invention to a vertical milling machine, such as shown in my Patent No. 2,259,472. In Fig. 3 I show in sectional plan view so much of a vertical milling machine as is necessary for an understanding of my invention. The milling machine has a vertical column I40 for supporting a knee I4I which is vertically movable along the column I40 in ways I42 formed on the column. The knee I" is provided with ways I43 along which a saddle- (not shown) is movable toward and away from the column I40. The said saddle supports a work table I44 on suitable ways so that the latter is movable to the left and right as shown in the drawing by means of a servomotor generally indicated at I40.

At I40 Is shown a typical work piece consisting of a concave forging of more or less elliptical shape, and in rough form having a raised blank face extending around its entire periphery. The machining operation I have chosen to illustrate my invention as controlling consists in forming a male flange on this blank face. A cutter I41 is rotated by any suitable means (not shown) and engages the work piece I40. It is the purpose of my invention to so control the relative movement between the work piece I40 and cutter I 4'! that the former will be accurately formed to a desired profile.

The work piece I40 is shown as being secured to a. fixture I42 by adjustable clamping means I40. Because of the nature of the machining operation to be performed the fixture I40 is mounted on a circular table I00, shown more clearly in Fig. 4, secured to the work table I44 and rotated at desired speed by a hydraulic motor I5I. In Fig. 3 I have shown the operative connections between the motor IliI and table I50 i gf 2 iii-s aid r th sca'imrr ertiit are piece In is com lepton pipe In. it a. Pf: as e ae a ls it -he ress reiapieet fi et eeathe ce J and somerset/111 increase, whereas movements of thgjollower iiiawayflom the nozzle I54will eii'ectcorrspon'ding' decreases in pressure within the pip -i Variations inpressurewith H pipe IBI control the diiiatibhbf massive-mates 145. Referring to Fig. 5, it will be observed lihat the pipe I6 I otrtoraheilows HIEthIlOlIQfiJBi pipe I64. Movements of the bellows ifiq g ontrol the,opera-, a pie wi m s u i fpump I55 driyegj'by motor" I 61; so

tween the'noz,

V H Qfinovablemem- ;;1 w the pilot Va'llfe gist isjffn the iiei 'tral }fsitioi j" the 'servo-irioto remains stai- 1H en;-however, th' f owerfl55ifapa the nozzle-154 th hie'mbeijjfl is positioned d nwardly of: upwardlj causing the servo-niot'or 45 td-p ltlpn work table I44 accordinglyfll'ffllhus, triplex.- amplejassbming the followerl55 to be positioned away from the nozzle likby virtue of a change in thecontour of the pattern I52, the servomptor' {Higgill position the 'worls table I44 in such a'di'rection as to restore'the' follower I55 to its original position relative to the nozzle I54. In the embodiment of my invention illustrated in Fig. 3, upon the follower I55 being positioned in a counterclockwise direction, thereby moving away from the nozzle I54, the servo-motor I" will operate to position the work table I44 to the left as viewed in the drawing until normal distance is restored between the follower I55 and nozzle I54. It is apparent that by proper shaping of the pattern I52 any desired contour may be cut on the work piece I48.

As shown in Fig. 3, the servo-motor I45 and the hydraulic circuits therefor, including the pilot valve I65, pump I86, and electric motor I61, are preferably arranged in a unit which may be conveniently mounted relative to the milling ma- I I t ere; it gs. we sa IE8? at prev/sear j e c dtliii-i I. t x ssrt htiigeae I l si i e.

tit e. ha lw s v 1 et i a we; 1" hamsse i fii t ES'FQQ l I-J thee! the;- imelle was t. l -ti e its antrell-j L 'iQQmE ePH HIQ ciflmptism a arms lli t natiellswse latter i sbmri emwi ap eis gm I see i alue tea -pate sse er ete the table, I5B.. 'l he-nozzlerll-l ls mounted omth marketable J y l l et l e stz-i erir swells m ses e 1 temewesm ei e 4mm evident that .s i; gastric am I'I is cireulari there willb no change .in the distancefbetygeen the follower m and thef -rio izle i-l'l in radius of the cam I15 w ill. h owc, helbafl el llr to 'move toward or f nozzle Ifli. H -P anpiied w ii w eis sse ai und erjpres'sure .from the ame. source as the no '1? J -I hro a Orifice ib hfistrlethm t e p'ieat vof h e lit ena ts-e exp nse m the variationsiin p essure ,withinl th e nozglgj i-lt to and from the hydraulic motor li t n ageor das with e p e ure at h -fin al witnirsei e I1 8 As explalnediwitli reference}? ther flntrol i slw n 01 54 one value Q1EQ UZQ th3 control unitv I15 is so arranged that's, maximum flow of hydrauli time to the: mot sv lilavei lrh r established. Asithe pressurevtithin pipe I18 i -t creases or decreases from this vaiue the eontrol, unit I19 will act to proportionately deergease the o Qt hydraulic fluid wa-the;metp fibzthereb z decreasing the rate of speed of the circular table I50.

The cam I15 may be shaped so that when the tool I41 and work piece I46 are relatively moved at maximum speed the bafile I12 is a normal distance from the nozzle Ill, and that when the desired shape of the work piece I46 is such that the relative speed between it and the tool I41 is desirably decreased, the radius of the cam I15 is either increased or decreased. By varying or shaping the cam to different radii at different points it is evident that the relative rate of movement between the tool I41 and work piece I45 may be varied as desired.

In Fig. 5 I have shown the control unit I19 diagrammatically and it comprises an adjustable fluid resistance I supplied with hydraulic fluid lows I83, to which pipe 118 is connected, positions the movable member 01' the fluid resistance I80 in accordance with variations in the shape of the cam or pattern 1.75.

Operation of the motor I82 may be controlled by a suitable switch I90. Also to stop or prevent operation of the motor I82 upon failure of air pressure the switch 169 may be, as shown, corinested in circuit with the motor I82. 7

Throughout the foregoing specification and in the claims to follow I have indicated that the work piece is formed to correspond to the profile or shape of the master. By such language I do not intend to imply that the work piece is brought to the exact shape 01' the master, but as will be evident to those familiar with the art the master will be formed so that the ultimate shape,

of the work piece produced is that desired, and that therefore the shape of thework piece will differ from that oi. the master by the amount oi angularity, etc. in the mechanism.

What I claim as new, and desire to secure by Letters Patent oi the United States, is:

1. In combination with a lathe having a rotatable live center, a hydraulic motor for rotating the live center, a carriage and a cross-slide mounted on said carriage, a nozzle having a port to atmosphere through which fluid is continuously discharged, means for variably throttling the discharge of fluid from said nozzle in accordance with the relative positions of said carriage and cross-slide to thereby produce corresponding variations in pressure in said nozzle, and means under the control of said pressure for regulating the speed of said motor.

2. In combination with a lathe having a rotatable llve center, a motor for rotating the live center a carriage and a cross-slide mounted on the carriage, a device movable with the carriage discharging a fluid to the atmosphere from a normally constant pressure source, means movable with the cross-slide controlling the discharge in accordance with the relative positions of said carriage and cross-slide to thereby produce corresponding variations in pressure of the fluid ahead of said device, and means under the control of said pressure for regulating the speed of said motor.

3. In combination with a machine tool having a rotatable work-holder and a tool holder, the work-holder and the tool-holder being constructed and arranged for relative bodily movement, a hydraulic motor for rotating the work-holder, fluid pressure means supplying fluid under pressure to said hydraulic motor, power means for relatively moving the work-holder and the toolholder, means for establishing a fluid pressure, independent of said fluid pressure supplied to said hydraulic motor, continuously corresponding to the.rela'tive position of the work-holder and the tool-holder. and means under the control of the independent pressure so established for varying the speedof the motor for rotating the workholder.

41. In combination with a lathe having a rotatable work-holder, a motor for rotating the workholder, a carriage and a cross-slide mounted on the carriage, means discharging a fluid to the atmosphere from a substantially constant pressure source, means controlling the discharge from said flrst means in accordance with the relative position of said carriage with respect to said cross-slide to thereby produce corresponding variations in pressure or the fluid ahead of said first means, one of said means being movable with the carriage and the other said means being movable with the cross-slide, and additional means controlled by the variation in pressure for regulating the speed of the motor.

5. In combination with a lathe having a rotatable work-hoider, a motor for rotating the workholder, a carriag and a cross-slide mounted on the carriage, means discharging air to the atmosphere from a substantially constant pressure source, means controlling the discharge from said first means in accordance with the relative positions of said carriage and cross-slide to thereby produce corresponding variations in pressure of the air ahead of said first means, one of said means being movable with the carriage and the other said means being movable with the crossslide, and additional means controlled by the variation in pressure for regulating the speed of the motor.

CLARENCE JOHNSON.

REFERENCES CITED The following references are of record in the flle of this patent:

UNITED STATES PATENTS Number Name Date 1,656,544 Thoma Jan. 17, 1928 1,961,089 Smith et ai May 29, 1934 2,209,037 Riegger July 23, 1940 1,871,752 Simonds Aug. 16, 1932 1,716,115 Clark et al. June 4, 1929 2,068,890 Sassen Jan. 26, 1937 1,709,674 Kuhl Apr. 16, 1929 2,271,598 Maurer Feb. 3, 1942 2,259,472 Johnson Oct. 21, 1941 2,025,748 Howe Dec. 31, 1935 2,150,032 Herman Mar. 7, 1939 FOREIGN PATENTS Number Country Date 513,715 Germany Dec, 1, 1930 

